CA2260415C - Steam cooled system in combined cycle power plant - Google Patents
Steam cooled system in combined cycle power plant Download PDFInfo
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- CA2260415C CA2260415C CA002260415A CA2260415A CA2260415C CA 2260415 C CA2260415 C CA 2260415C CA 002260415 A CA002260415 A CA 002260415A CA 2260415 A CA2260415 A CA 2260415A CA 2260415 C CA2260415 C CA 2260415C
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- Prior art keywords
- steam
- temperature
- cooling
- gas turbine
- pressure
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
- F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
- F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
- F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
- F01K23/106—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
- F01K23/108—Regulating means specially adapted therefor
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E20/00—Combustion technologies with mitigation potential
- Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
- Y02P80/00—Climate change mitigation technologies for sector-wide applications
- Y02P80/10—Efficient use of energy, e.g. using compressed air or pressurized fluid as energy carrier
- Y02P80/15—On-site combined power, heat or cool generation or distribution, e.g. combined heat and power [CHP] supply
Abstract
Gas turbine steam cooled system is constructed such that high temperature portion outlet steam temperature is maintained to predetermined value without cooling steam pressure becoming lower than pressure in gas turbine cylinder.
Steam coming from intermediate pressure superheater 10 of waste heat recovery boiler 2 is led into high temperature portion 8 of gas turbine for cooling thereof . Temperature of cooling steam at outlet of the high temperature portion 8 is detected by high temperature portion outlet steam temperature detector 15 and signal thereof is sent to lower value selector 19 via temperature controller 11. Pressure in gas turbine cylinder is detected by gas turbine cylinder pressure detector 17 and pressure of the cooling steam at the high temperature portion 8 outlet is detected by high temperature portion outlet steam pressure detector 16 and differential signal thereof is sent to pressure controller 18. Signal from the temperature controller 11 and that from the pressure controller 18 are inputted into the lower value selector 19 and temperature control valve 12 is controlled by the lower value thereof to be opened and closed.
Steam coming from intermediate pressure superheater 10 of waste heat recovery boiler 2 is led into high temperature portion 8 of gas turbine for cooling thereof . Temperature of cooling steam at outlet of the high temperature portion 8 is detected by high temperature portion outlet steam temperature detector 15 and signal thereof is sent to lower value selector 19 via temperature controller 11. Pressure in gas turbine cylinder is detected by gas turbine cylinder pressure detector 17 and pressure of the cooling steam at the high temperature portion 8 outlet is detected by high temperature portion outlet steam pressure detector 16 and differential signal thereof is sent to pressure controller 18. Signal from the temperature controller 11 and that from the pressure controller 18 are inputted into the lower value selector 19 and temperature control valve 12 is controlled by the lower value thereof to be opened and closed.
Description
SPECIFICATION
STEAM COOLED SYSTEM IN COMBINED CYCLE POWER PLANT
BACKGROUND OF THE INVENTION:
Field of the Invention:
The present invention relates generally to a steam cooled system in a combined cycle power plant and more specifically to that constructed such that a high temperature portion (portion to be cooled) of gas turbine combustor etc.
in a combined cycle power plant in which a gas turbine plant and a steam turbine plant are combined together is cooled by steam coming from a waste heat recovery boiler.
Description of the Prior Art:
In a combined cycle power plant in which a gas turbine plant and a steam turbine plant are combined together, a high temperature range of the thermal energy is taken charge of by a gas turbine and a low temperature range thereof by a steam turbine, respectively, so that the thermal energy is recovered to be used effectively, hence a high attention is being paid to this power system recently.
In this combined cycle power plant, as one measure for enhancing the efficiency, in place of using air as cooling medium for cooling the gas turbine high temperature portion, a system using steam generated in the bottoming cycle is being disclosed.
Fig. 3 shows a prior art gas turbine steam system in a combined cycle power plant. In Fig. 3, numeral 1 designates a gas turbine, numeral 2 designates a waste heat recovery boiler thereof, numeral 3 designates a high pressure steam turbine and numeral 4 designates an intermediate pressure steam turbine.
The waste heat recovery boiler 2 comprises a high pressure drum 5, a high pressure superheater 6, a reheater 7, an intermediate pressure drum 9, an intermediate pressure superheater 10, etc.
Numeral 8 designates a high temperature portion (or a heat exchanger therefor ) of gas turbine combustor etc . , which is a portion to be cooled by steam.
Numeral 12 designates a temperature control valve, which is controlled by a temperature control device 11 . Numeral 13 designates a superheater outlet steam temperature detector and numeral 15 designates a high temperature portion outlet steam temperature detector.
In the gas turbine steam system shown in Fig. 3, exhaust gas of the gas turbine 1 is led into the waste heat recovery boiler 2. Steam from the high pressure drum 5 of the waste heat recovery boiler 2 is led into the high pressure steam turbine 3 via the high pressure superheater 6. Also, steam from the intermediate pressure drum 9 is led into the intermediate pressure steam turbine 4 via the intermediate pressure superheater 10 and the reheater 7 sequentially. Outlet steam of the high pressure steam turbine 3 joins in an inlet steam of the reheater 7.
On the other hand, outlet steam of the intermediate pressure superheater 10 diverges partly from that led to the reheater 7 to flow through the temperature control valve 12 and the high temperature portion 8 of the gas turbine combustor etc .
sequentially and then joins in the outlet steam of the reheater 7 to be led into the intermediate pressure steam turbine 4.
Output of the high temperature portion outlet steam temperature detector 15 which is provided at an outlet of the high temperature portion 8 is sent to the temperature control valve 12 which is provided in a steam line on an inlet side of the high temperature portion 8 via the temperature control device 11.
Thus, the exhaust gas of the gas turbine 1 enters the waste heat recovery boiler 2 to generate a high pressure steam, an intermediate pressure steam and a low pressure steam. The steam generated at the high pressure drum 5 becomes a superheated steam at the high pressure superheater 6 to work at the high pressure steam turbine 3 and flows through a high pressure exhaust steam line to join in the intermediate pressure steam and then is reheated at the reheater 7 to be led into the intermediate pressure steam turbine 4. Steam generated at the intermediate pressure drum 9 is superheated at the intermediate pressure superheater 10 and is led in a necessary amount to the high temperature portion 8 of the gas turbine 1 combustor etc. for cooling thereof either through a heat exchanger or directly in the high temperature portion 8 and then joins in the outlet steam of the reheater 7. Surplus steam joins in the steam coming from the high pressure steam turbine 3 through the high pressure exhaust steam line to be led to the reheater 7.
As to the steam which has passed through the high temperature portion 8, temperature thereof is controlled such that the temperature control valve 12 , which is provided in the steam line on the inlet side of the high temperature portion 8, is controlled by a control signal from the high temperature portion outlet steam temperature detector 15 and the temperature control device 11 so that flow rate of the steam is controlled.
Said prior art steam cooled system is a system in which the steam used for cooling of the high temperature portion 8 of the gas turbine combustor etc. is controlled of its flow rate by the temperature control valve 12 provided at an inlet of the high temperature portion 8 so that the outlet steam temperature of the high temperature portion 8 is set to a predetermined value.
In this case, if a cooling steam pressure becomes lower than pressure in a turbine cylinder of the gas turbine 1 (discharge pressure of gas turbine air compressor), combustion gas comes in the steam system and there arises a fear of occurrence of problem, such as burning of the steam system etc.
That is, in the prior art system in which the temperature control valve 12 is provided at the inlet of the high temperature portion 8, while it is possible to do control for suppressing rise of the outlet steam temperature of the high temperature portion 8 , there is a problem that it is dif f icult to do control for the case where the cooling steam pressure becomes lower than the pressure in the turbine cylinder (discharge pressure of gas turbine air compressor).
Also, in the prior art steam cooled system in the combined cycle power plant, while a basic framework of control of gas turbine operation is maintained such that the gas turbine is operated safely by a fuel flow control valve being controlled by a valve opening command signal which is made by the lowest value out of fuel flow rate command signals given from a speed governing device (output control device), a combustion temperature control device, a load limit control device and an acceleration control device, there is no sufficient one yet of flow rate control of the cooling steam for cooling the high temperature portion of the gas turbine.
That is, in the gas turbine employing the steam cooled system, as there is a need to prevent unusual excess cooling or heating and to suppress occurrence of thermal stress at the gas turbine high temperature portion, it is necessary to do control of the steam supply rate so as to effect an appropriate cooling corresponding to the thermal load at the gas turbine high temperature portion.
SUMMARY OF THE INVENTION:
In order to solve the problem in the relation of the cooling steam pressure and the pressure in the turbine cylinder in the prior art gas turbine steam cooled system in which the gas turbine high temperature portion is cooled by steam from the waste heat recovery boiler, it is a first object of the present invention to provide a gas turbine steam cooled system which is constructed such that there is no case of the cooling steam pressure becoming lower than the pressure in the gas turbine cylinder and temperature rise of the high temperature portion outlet steam is suppressed as much as possible.
Based on the inventors' experience and knowledge as heretofore obtained that the fuel flow rate, being very sensitively influenced by change in the thermal load, may be employed as a control factor, it is a second object of the present invention to provide a steam cooled system in the combined cycle power plant which is constructed such that supply of the cooling steam into the gas turbine high temperature portion is controlled appropriately corresponding to the thermal load at the gas turbine high temperature portion.
STEAM COOLED SYSTEM IN COMBINED CYCLE POWER PLANT
BACKGROUND OF THE INVENTION:
Field of the Invention:
The present invention relates generally to a steam cooled system in a combined cycle power plant and more specifically to that constructed such that a high temperature portion (portion to be cooled) of gas turbine combustor etc.
in a combined cycle power plant in which a gas turbine plant and a steam turbine plant are combined together is cooled by steam coming from a waste heat recovery boiler.
Description of the Prior Art:
In a combined cycle power plant in which a gas turbine plant and a steam turbine plant are combined together, a high temperature range of the thermal energy is taken charge of by a gas turbine and a low temperature range thereof by a steam turbine, respectively, so that the thermal energy is recovered to be used effectively, hence a high attention is being paid to this power system recently.
In this combined cycle power plant, as one measure for enhancing the efficiency, in place of using air as cooling medium for cooling the gas turbine high temperature portion, a system using steam generated in the bottoming cycle is being disclosed.
Fig. 3 shows a prior art gas turbine steam system in a combined cycle power plant. In Fig. 3, numeral 1 designates a gas turbine, numeral 2 designates a waste heat recovery boiler thereof, numeral 3 designates a high pressure steam turbine and numeral 4 designates an intermediate pressure steam turbine.
The waste heat recovery boiler 2 comprises a high pressure drum 5, a high pressure superheater 6, a reheater 7, an intermediate pressure drum 9, an intermediate pressure superheater 10, etc.
Numeral 8 designates a high temperature portion (or a heat exchanger therefor ) of gas turbine combustor etc . , which is a portion to be cooled by steam.
Numeral 12 designates a temperature control valve, which is controlled by a temperature control device 11 . Numeral 13 designates a superheater outlet steam temperature detector and numeral 15 designates a high temperature portion outlet steam temperature detector.
In the gas turbine steam system shown in Fig. 3, exhaust gas of the gas turbine 1 is led into the waste heat recovery boiler 2. Steam from the high pressure drum 5 of the waste heat recovery boiler 2 is led into the high pressure steam turbine 3 via the high pressure superheater 6. Also, steam from the intermediate pressure drum 9 is led into the intermediate pressure steam turbine 4 via the intermediate pressure superheater 10 and the reheater 7 sequentially. Outlet steam of the high pressure steam turbine 3 joins in an inlet steam of the reheater 7.
On the other hand, outlet steam of the intermediate pressure superheater 10 diverges partly from that led to the reheater 7 to flow through the temperature control valve 12 and the high temperature portion 8 of the gas turbine combustor etc .
sequentially and then joins in the outlet steam of the reheater 7 to be led into the intermediate pressure steam turbine 4.
Output of the high temperature portion outlet steam temperature detector 15 which is provided at an outlet of the high temperature portion 8 is sent to the temperature control valve 12 which is provided in a steam line on an inlet side of the high temperature portion 8 via the temperature control device 11.
Thus, the exhaust gas of the gas turbine 1 enters the waste heat recovery boiler 2 to generate a high pressure steam, an intermediate pressure steam and a low pressure steam. The steam generated at the high pressure drum 5 becomes a superheated steam at the high pressure superheater 6 to work at the high pressure steam turbine 3 and flows through a high pressure exhaust steam line to join in the intermediate pressure steam and then is reheated at the reheater 7 to be led into the intermediate pressure steam turbine 4. Steam generated at the intermediate pressure drum 9 is superheated at the intermediate pressure superheater 10 and is led in a necessary amount to the high temperature portion 8 of the gas turbine 1 combustor etc. for cooling thereof either through a heat exchanger or directly in the high temperature portion 8 and then joins in the outlet steam of the reheater 7. Surplus steam joins in the steam coming from the high pressure steam turbine 3 through the high pressure exhaust steam line to be led to the reheater 7.
As to the steam which has passed through the high temperature portion 8, temperature thereof is controlled such that the temperature control valve 12 , which is provided in the steam line on the inlet side of the high temperature portion 8, is controlled by a control signal from the high temperature portion outlet steam temperature detector 15 and the temperature control device 11 so that flow rate of the steam is controlled.
Said prior art steam cooled system is a system in which the steam used for cooling of the high temperature portion 8 of the gas turbine combustor etc. is controlled of its flow rate by the temperature control valve 12 provided at an inlet of the high temperature portion 8 so that the outlet steam temperature of the high temperature portion 8 is set to a predetermined value.
In this case, if a cooling steam pressure becomes lower than pressure in a turbine cylinder of the gas turbine 1 (discharge pressure of gas turbine air compressor), combustion gas comes in the steam system and there arises a fear of occurrence of problem, such as burning of the steam system etc.
That is, in the prior art system in which the temperature control valve 12 is provided at the inlet of the high temperature portion 8, while it is possible to do control for suppressing rise of the outlet steam temperature of the high temperature portion 8 , there is a problem that it is dif f icult to do control for the case where the cooling steam pressure becomes lower than the pressure in the turbine cylinder (discharge pressure of gas turbine air compressor).
Also, in the prior art steam cooled system in the combined cycle power plant, while a basic framework of control of gas turbine operation is maintained such that the gas turbine is operated safely by a fuel flow control valve being controlled by a valve opening command signal which is made by the lowest value out of fuel flow rate command signals given from a speed governing device (output control device), a combustion temperature control device, a load limit control device and an acceleration control device, there is no sufficient one yet of flow rate control of the cooling steam for cooling the high temperature portion of the gas turbine.
That is, in the gas turbine employing the steam cooled system, as there is a need to prevent unusual excess cooling or heating and to suppress occurrence of thermal stress at the gas turbine high temperature portion, it is necessary to do control of the steam supply rate so as to effect an appropriate cooling corresponding to the thermal load at the gas turbine high temperature portion.
SUMMARY OF THE INVENTION:
In order to solve the problem in the relation of the cooling steam pressure and the pressure in the turbine cylinder in the prior art gas turbine steam cooled system in which the gas turbine high temperature portion is cooled by steam from the waste heat recovery boiler, it is a first object of the present invention to provide a gas turbine steam cooled system which is constructed such that there is no case of the cooling steam pressure becoming lower than the pressure in the gas turbine cylinder and temperature rise of the high temperature portion outlet steam is suppressed as much as possible.
Based on the inventors' experience and knowledge as heretofore obtained that the fuel flow rate, being very sensitively influenced by change in the thermal load, may be employed as a control factor, it is a second object of the present invention to provide a steam cooled system in the combined cycle power plant which is constructed such that supply of the cooling steam into the gas turbine high temperature portion is controlled appropriately corresponding to the thermal load at the gas turbine high temperature portion.
Further, it is a third object of the present invention to provide a monitoring system in the combined cycle power plant employing the steam cooled system of the high temperature portion, such as combustor etc. , which is constructed such that the outlet steam temperature of the high temperature portion is detected to find occurrence of disorder in the high temperature portion earlier so that the gas turbine may be operated safely.
In order to attain said first object, the present invention provides a steam cooled system in a combined cycle power plant constructed such that there is provided a temperature control valve at a cooling steam outlet of a high temperature portion of gas turbine and said temperature control valve performs a cooling steam temperature control so that temperature of cooling steam coming out of said high temperature portion is set to a predetermined value as well as performs a cooling steam pressure control, which is preferential to said cooling steam temperature control, so that pressure of the cooling steam coming out of said high temperature portion may not become lower than pressure in a turbine cylinder of said gas turbine.
In said steam cooled system according to the present invention, if the cooling steam pressure is going to become lower than the pressure in the gas turbine cylinder (discharge pressure of gas turbine air compressor), even if the outlet steam temperature of the high temperature portion is higher than the predetermined value, the cooling steam pressure control is preferential to the cooling steam temperature control and there occurs no case that the temperature control valve provided at the cooling steam outlet of the high temperature portion opens beyond the opening at that time, hence the cooling steam pressure by no means lowers further and is maintained higher than the pressure in the gas turbine cylinder (discharge pressure of gas turbine air compressor).
Said steam cooled system according to the present invention may be constructed such that there are provided a cooling steam temperature control system for controlling said temperature control valve so that a cooling steam temperature at said cooling steam outlet is set to a predetermined value and a cooling steam pressure control system for controlling said temperature control valve so that a cooling steam pressure at said cooling steam outlet may not become lower than pressure in a turbine cylinder of said gas turbine and said temperature control valve is operated by a lower value out of control signals of said temperature control system and said pressure control system.
In the gas turbine steam cooled system constructed as above, if the cooling steam pressure is going to become lower than the pressure in the gas turbine cylinder (discharge pressure of gas turbine air compressor), because the _ g _ temperature control valve provided at the cooling steam outlet of the high temperature portion is controlled by the lower value out of the two control signals, there occurs no case that the temperature control valve opens beyond the opening at that time even if the outlet steam temperature of the high temperature portion is higher than the predetermined value, and the cooling steam pressure by no means lowers further.
Thus, the cooling steam pressure is maintained higher than the pressure in the gas turbine cylinder (discharge pressure of gas turbine air compressor) and the high temperature portion can be cooled within the range of the cooling steam pressure not becoming lower than the pressure in the gas turbine cylinder.
Further, in order to attain said second object, the present invention provides a steam cooled system in a combined cycle power plant constructed such that there is provided a control device for controlling a flow rate of cooling steam supplied into said steam cooled system, based on an outlet steam temperature of said steam cooled system and a fuel supply rate to said gas turbine.
That is, in view of the fact that the thermal load of the gas turbine high temperature portion to be cooled changes corresponding to the fuel supply rate to the gas turbine and yet the speed of such change is quick with a sensitive response, the fuel supply rate of the fuel supplied into the gas turbine _ g _ is made one control factor and in addition thereto, the outlet steam temperature of the steam cooled system is made another control factor, thus the steam flow rate of the cooling steam supplied into the steam cooled system is controlled appropriately.
In the combined cycle power plant employing the steam cooled system, it is preferable that occurrence of disorder, such as occurrence of cracks, clogging of steam system or the like, in the gas turbine high temperature portion is detected earlier by use of a temperature detecting signal of a high temperature portion outlet steam temperature detector so that a safe operation of the gas turbine may be effected.
Thus, the present invention provides an outlet steam monitoring system in a steam cooled type gas turbine, said steam cooled type gas turbine being constructed such that a cooling steam is supplied into a high temperature portion of combustor, blade or the like and the cooling steam after being used for cooling is recovered, characterized ir. 'hat there are provided a temperature detector for detecting an outlet temperature of 2~ said steam after being used for cooling and a control device which, being inputted a detected signal of said temperature detector for comparison with a predetermined temperature value, puts out a warning signal as well as a signal for throttling opening of a fuel flow control valve to a predetermined opening or a signal for closing a shut-off valve, if a detected temperature of said temperature detector exceeds said predetermined temperature value.
In the outlet steam monitoring system of the present invention, the outlet steam temperature of the steam which has cooled the high temperature portion is detected by the temperature detector and this detected signal is inputted into the control device. In the control device, the outlet steam temperature at the normal state, the temperature at the dangerous state, the upper limit temperature to shut off the fuel, etc. are set in advance and the detected temperature is compared therewith. If the detected temperature exceeds the set temperature, the warning signal, the signal for throttling the opening of the flow control valve and the signal for closing the shut-off valve are put out corresponding to the respective level of the temperature rise. Thereby, disorder in the high temperature portion is detected earlier and a dangerous state can be avoided by said signals of the control device.
BRIEF DESCRIPTION OF THE DRAWINGS:
Fig. 1 is a diagrammatic view showing construction of a steam cooled system in a combined cycle power plant of embodiment 1 according to the present invention.
Fig. 2 is a view of a cooling steam supply system and control system of gas turbine high temperature portion in a steam cooled system of embodiment 2 according to the present invention, wherein Fig. 2 ( a ) is a schematic view of arrangement of main components of the cooling steam supply system and Fig.
2(b) is a schematic view of a control circuit.
Fig. 3 is a diagrammatic view showing construction of a prior art steam cooled system in a combined cycle power plant.
Fig. 4 is a constructional view of an outlet steam monitoring system in a steam cooled type gas turbine of embodiment 3 according to the present invention.
Fig. 5 is a graph showing relationship between temperature states and control signals in the outlet steam monitoring system of the embodiment 3, wherein Fig. 5(a) shows the temperature states and Fig. 5(b) shows the control signals.
DESCRIPTION OF THE PREFERRED EMBODIMENTS:
Herebelow, a steam cooled system of the combined cycle power plant according to the present invention will be described concretely based on embodiments 1 and 2 shown in Figs .
1 and 2. It is to be noted that, in the embodiments below, same parts or components as those in the prior art shown in Fig. 3 are given same reference numerals for ease of description.
(Embodiment 1) Firstly, embodiment 1 shown in Fig. 1 will be described. In Fig. 1, a temperature control valve 12 is provided on an outlet side of cooling steam of a high temperature portion 8, such as combustor etc. Numeral 16 designates a high temperature portion outlet steam pressure detector and numeral 17 designates a gas turbine cylinder pressure detector. Construction thereof is made such that signals from these pressure detectors 16, 17 are given to a subtractor 20.
Numeral 18 designates a pressure controller, which receives output signal from the subtractor 20. Numeral 19 designates a lower value selector, which receives signals from a temperature controller 11 and the pressure controller 18 to select a lower value thereof. Other portions of the construction thereof are substantially same as those of the gas turbine steam cooled system shown in Fig. 3 and description thereon will be omitted.
In the gas turbine steam cooled system of Fig. 1 constructed as mentioned above, a signal showing a cooling steam temperature detected at a high temperature portion outlet steam temperature detector 15 is sent to the temperature controller 11 and the temperature control valve 12 is adjusted so as to set a high temperature portion outlet steam temperature to a predetermined set value.
That is, the temperature controller 11 generates a signal such that, if the cooling steam temperature at an outlet of the high temperature portion 8 is higher than the set value, the temperature control valve 12 is operated in the direction to open to increase flow rate of the cooling steam or reversely if the cooling steam temperature at the outlet of the high temperature portion 8 is lower than the set value, the temperature control valve 12 is operated in the direction to close to decrease the flow rate of the cooling steam.
On the other hand, a cooling steam pressure at the outlet of the high temperature portion 8 is detected by the pressure detector 16 and pressure in a gas turbine cylinder (discharge pressure of gas turbine air compressor) is detected by the pressure detector 17, respectively, and respective signals showing such measured pressures are inputted into the subtractor 20 to be subtracted therein. If there is recognized a tendency that the cooling steam pressure becomes lower than the pressure in the turbine cylinder, the pressure controller 18 generates a signal such that the temperature control valve 12 is operated in the direction to close.
The respective signals sent from the temperature controller 11 and the pressure controller 18 are inputted into the lower value selector 19 to be compared of their sizes and the lower value is selected to be put out as a signal to operate the temperature control valve 12. By use of the lower value selector 19 selecting the signals of the temperature controller 11 and the pressure controller 18, the temperature controller 11 can do control such that a rise of the cooling steam temperature at the outlet of the high temperature portion 8 is suppressed as much as possible within the range of the outlet steam pressure of the high temperature portion 8 not becoming lower than the pressure in the gas turbine cylinder.
(Embodiment 2) Next, embodiment 2 shown in Fig. 2 will be described.
In Fig. 2, only a construction around the gas turbine high temperature portion to be cooled by steam is shown and other - portions of the construction of the combined cycle power plant being substantially same as those shown in Fig. 1, description thereon will be omitted.
Fig. 2 ( a ) shows a portional equipment arrangement in a main part of a cooling steam flow. Numeral 21 designates a cooling steam supply passage, which supplies therethrough a high pressure turbine exhaust steam or a generated steam of a waste heat recovery boiler etc. (not shown) as a cooling steam.
Numeral 22 designates a temperature control valve provided in the cooling steam supply passage 21, which is controlled to be opened and closed by an opening and closing command E obtained in a control circuit as described later.
Numeral 23 designates a combustor disposed subsequently to the temperature control valve 22, numeral 24 designates a pressure control valve provided in a cooling steam recovery passage 27 and numeral 25 designates a pressure control valve provided in a condenser connection passage 26 which connects to a condenser (not shown).
Fig. 2 ( b ) shows a control circuit for generating said opening and closing command E, wherein an input command on one hand is a fuel control signal CSO (Control signal output) for controlling flow rate of fuel supplied into the combustor 23 and this fuel control signal CSO is first computed by function units 30, 31, 32 and 33, respectively.
Also, an input command on the other hand is an outlet steam temperature (actual temperature) of the combustor 23 and computation is done at a computing unit 34 which performs a proportional integration together with signals based on outputs of the function units 32, 33 and result thereof is added at an adder 35 to signals based on outputs of the function units 30, 31 so that said opening and closing command E is generated.
It is to be noted that the fuel control signal CSO
is corrected corresponding to a temperature of air charged for combustion etc . and an opening command value and a temperature set value of the temperature control valve 22 are decided based thereon so that a sudden change in the fuel control signal CSO
may be followed up well.
Also, the opening command value and the temperature set value, respectively, may be changed instantly by a fuel change-over command so that a change of the fuel may be followed up quickly.
Also, the temperature set value is computed in comparison with the actual temperature by a proportional integration computation (PI control) or by a proportional computation (P control) and result thereof is added to the opening command value, wherein there is set an upper limit in a direction of throttling and if the opening command is in saturation (100 or more), output of the proportional integration computation (PI) or the like is fixed to that value.
According to the present embodiment mentioned above, the cooling steam flow rate is controlled advance-wise based on a certain function setting corresponding to the fuel supply rate into the gas turbine. Thus, while in the method, for example, where the cooling steam flow rate is controlled relying only on the temperature of the cooling steam which has been used for cooling of the high temperature portion, there is a fear of delay due to thermal capacity of pipings etc.
downstream of the high temperature portion, there is no such a fear in the present embodiment and unusual excess cooling or heating can be prevented and a favorable cooling by steam, which suppresses occurrence of thermal stresses at the high temperature portion to be cooled, can be realized.
(Embodiment 3) An example as embodiment 3 where a monitoring system is constructed for monitoring an outlet steam temperature of a steam cooled type gas turbine using a temperature detecting signal of a combustor etc. high temperature portion outlet steam temperature detector will be described with reference to Figs. 4 and 5.
In Fig. 4, numeral 41 designates a steam supply manifold and numeral 42 designates a flow control valve, which controls flow rate of steam to be supplied. Numeral 43 designates a supply line, which supplies therethrough a cooling steam into a cooling steam supply pipe 65 of each of a plurality of combustor main bodies 60 from the steam supply manifold 41.
Numeral 44 designates a recovery line, numeral 45 designates a steam recovery manifold and steam recovered through the recovery line 44 from cooling steam recovery pipes 66, 67 of each of the plurality of combustor main bodies 60 is recovered into the steam recovery manifold 45.
Numeral 46 designates a temperature detector, which detects temperature of inlet steam flowing through the supply line 43 connecting to each of the plurality of combustor main bodies 60 to send a signal thereof to a control device 50 via an inlet steam temperature detecting line 47. Numeral 48 also designates a temperature detector, which detects temperature of the steam recovered flowing through the recovery line 44 from the cooling steam recovery pipes 66, 67 to send a signal thereof to the control device 50 via an outlet steam temperature detecting line 49.
Numeral 50 designates the control device mentioned above, numeral 51 designates a display for displaying result of computation at the control device 50 and numeral 52 designates a warning device for giving a warning by an alarm etc. when something wrong is found as the result of computation at the control device 50. Numeral 53 designates a control signal line, wherein a line 53a thereof transmits therethrough a signal to control opening of a flow control valve 55 of a fuel system 54 and a line 53b thereof transmits therethrough a signal to control opening and closing of a shut-off valve 56.
In the construction mentioned above, an inlet steam temperature detected by the temperature detector 46 of each of the combustors as the high temperature portions and an outlet steam temperature detected by the temperature detector 48 of the steam recovered from the cooling steam recovery pipes 66, 67 of each of the combustors are inputted into the control device 50.
Temperature of the steam supplied is approximately a planned supply steam temperature and temperature of the steam recovered is approximately a planned outlet steam temperature at a normal operation time. The control device 50 confirms whether the inlet steam temperature is normal as being approximately the planned supply steam temperature or not and then monitors the outlet steam temperature. While the outlet steam temperature is approximately the planned outlet steam temperature at the normal operation time, if there occurs an unusual case, such as clogging of steam passage, occurrence of cracks or the like, in the combustor main body, the temperature rises to a dangerous level or more to cause a dangerous situation, hence the control is done such that the situation of temperature is displayed on the display 51 as well as the signal thereof is sent to the warning device 52 so as to generate a warning.
If the situation of rising of the temperature continues, the control device 50 sends a control signal through the control signal line 53b to throttle opening of the flow control valve 55 so that the fuel in the fuel system is decreased to control the load, and if the temperature rises further to become higher than an upper limit temperature, for example a shut-off temperature, a control signal is put out through the control signal line 53a to control the shut-off valve 56 to be closed and the gas turbine is tripped.
Fig. 5 is an explanatory view of the situation mentioned above, wherein Fig. 5 ( a ) shows changes in the outlet steam temperature and Fig. 5(b) shows control signals corresponding to the temperature. In Fig. 5(a), the outlet steam temperature is in the state of approximately the planned outlet steam temperature at the normal operation time as shown by (X), and if the temperature rises beyond the dangerous temperature at time t1 as shown by ( Y1 ) , the control device 50 recognizes a dangerous situation of the combustor main body 60 to put out a warning signal (S1) as shown in Fig. 5(b) continuously during the time t1 to t2 exceeding the dangerous temperature and the warning device 51 is operated.
If the temperature continues to rise for a certain time until time t1' between the time t, to t2, the control device puts out a load decreasing signal (S,) as shown in Fig. 5(b) to control opening of the flow control valve 55 of the fuel system 54 to be throttled. If the temperature rises further to exceed the shut-off temperature at time t3 as shown by (YZ), a shut-off signal (S2) as shown in Fig. 5(b) is put out to close the shut-off valve 56 of the fuel system 54 so that fuel supply to a main fuel supply pipe 63 is stopped and the gas turbine is tripped.
It is to be noted that although the illustration of Fig. 4 is made in a form of omission on the example where the plurality of the combustor main bodies 60 are arranged in the common fuel system 54 to control the flow control valve 55 and the shut-off valve 56 commonly, needless to mention, it is necessary to control the flow control valve and the shut-off valve of the respective fuel system independently with respect to each of the combustor main bodies 60, wherein accident or disorder of each of the combustors is detected, flow rate of only the combustor on which disorder has been detected is controlled and the shut-off valve thereof is closed.
Also, in the present embodiment, although the example of the steam cooled combustor has been described, the invention is not limited thereto but may be applied to a temperature monitoring of an object to be cooled not only of the combustor but also of a stationary blade and a moving blade with same function and effect.
According to the present embodiment, temperature of the outlet steam recovered through the recovery line 44 from the cooling steam recovery pipes 66, 67 of the combustor main body 60 is detected by the temperature detector 48 to be inputted into the control device 50 so that the temperature rise is monitored by the control device 50 and if the outlet steam temperature exceeds the predetermined temperature, the warning device 52 is operated to generate a warning as well as the flow control valve 55 is controlled to control the fuel flow rate or to close the shut-off valve 56 to stop the fuel supply, thereby disorder of the combustor can be detected earlier by the change in the outlet steam temperature and a safe operation of the gas turbine can be ensured.
As described above with respect to the embodiments 1 and 2, in the steam cooled system of the combined cycle power plant according to the present invention, the construction is made such that there is provided the temperature control valve - at the cooling steam outlet of the high temperature portion of the gas turbine and this temperature control valve performs a cooling steam temperature control so that the temperature of the cooling steam coming out of the high temperature portion is set to the predetermined value as well as performs a cooling steam pressure control, which is preferential to said cooling steam temperature control, so that the pressure of the cooling steam coming out of the high pressure portion may not become lower than the pressure in the gas turbine cylinder.
According to this gas turbine steam cooled system, it is possible to effect a cooling by steam so that the temperature of the cooling steam coming out of the gas turbine high temperature portion may not become higher than the predetermined temperature within the range of the cooling steam pressure not becoming lower than the pressure in the gas turbine cylinder.
Also, according to the present invention constructed such that there are provided the cooling steam temperature control system for controlling the temperature control valve so that the cooling steam temperature at the cooling steam outlet of the gas turbine high temperature portion is set to the predetermined set value and the cooling steam pressure control system for controlling the temperature control valve so that the cooling steam pressure at the cooling steam outlet may not become lower than the pressure in the gas turbine cylinder and the temperature control valve is operated by the lower value out of the signals of these two control systems, a device in which the cooling steam pressure is securely maintained higher than the pressure in the gas turbine cylinder in preference to the control of the cooling steam temperature at the outlet of the gas turbine high temperature portion by a simple construction can be realized.
Also, according to the present invention constructed otherwise, based on the experience and knowledge of the inventors here that the thermal load of the gas turbine high temperature portion to be cooled changes corresponding to the fuel supply rate and the speed of such change is comparatively quick, the construction is made such that the cooling steam side is also controlled with a good response corresponding to the fuel supply rate. That is, according to this invention, the fuel supply rate to the gas turbine and the outlet steam temperature of the steam cooled system are employed as the control factors and the flow rate of the steam supplied into the steam cooled system is controlled appropriately so that the gas turbine high temperature portion may not be cooled or heated excessively and occurrence of the thermal stresses at said high temperature portion may be suppressed. Hence, a device which can be operated safely and stably for a long time is realized and a reliability of the plant can be enhanced remarkably.
Further, as described concretely based on the embodiment 3 , the outlet steam monitoring system according to the present invention is used in the steam cooled type gas turbine which is constructed such that the cooling steam is supplied into the high temperature portion of combustor, blade or the like and the cooling steam after used for cooling is recovered, and is characterized in that there are provided the temperature detector for detecting the outlet temperature of the steam after used for cooling and the control device which, being inputted a detected signal of the temperature detector for comparison with the predetermined temperature value, puts out a warning signal as well as a signal for throttling opening of the fuel flow control valve to the predetermined opening or a signal for closing the shut-off valve, if a detected temperature of the temperature detector exceeds the predetermined temperature value. By employing such construction, upon the change in the outlet temperature of the steam after used for the cooling, disorder of the high temperature portion can be detected earlier as well as the control signal can be put out from the control device so that danger may be avoided.
In order to attain said first object, the present invention provides a steam cooled system in a combined cycle power plant constructed such that there is provided a temperature control valve at a cooling steam outlet of a high temperature portion of gas turbine and said temperature control valve performs a cooling steam temperature control so that temperature of cooling steam coming out of said high temperature portion is set to a predetermined value as well as performs a cooling steam pressure control, which is preferential to said cooling steam temperature control, so that pressure of the cooling steam coming out of said high temperature portion may not become lower than pressure in a turbine cylinder of said gas turbine.
In said steam cooled system according to the present invention, if the cooling steam pressure is going to become lower than the pressure in the gas turbine cylinder (discharge pressure of gas turbine air compressor), even if the outlet steam temperature of the high temperature portion is higher than the predetermined value, the cooling steam pressure control is preferential to the cooling steam temperature control and there occurs no case that the temperature control valve provided at the cooling steam outlet of the high temperature portion opens beyond the opening at that time, hence the cooling steam pressure by no means lowers further and is maintained higher than the pressure in the gas turbine cylinder (discharge pressure of gas turbine air compressor).
Said steam cooled system according to the present invention may be constructed such that there are provided a cooling steam temperature control system for controlling said temperature control valve so that a cooling steam temperature at said cooling steam outlet is set to a predetermined value and a cooling steam pressure control system for controlling said temperature control valve so that a cooling steam pressure at said cooling steam outlet may not become lower than pressure in a turbine cylinder of said gas turbine and said temperature control valve is operated by a lower value out of control signals of said temperature control system and said pressure control system.
In the gas turbine steam cooled system constructed as above, if the cooling steam pressure is going to become lower than the pressure in the gas turbine cylinder (discharge pressure of gas turbine air compressor), because the _ g _ temperature control valve provided at the cooling steam outlet of the high temperature portion is controlled by the lower value out of the two control signals, there occurs no case that the temperature control valve opens beyond the opening at that time even if the outlet steam temperature of the high temperature portion is higher than the predetermined value, and the cooling steam pressure by no means lowers further.
Thus, the cooling steam pressure is maintained higher than the pressure in the gas turbine cylinder (discharge pressure of gas turbine air compressor) and the high temperature portion can be cooled within the range of the cooling steam pressure not becoming lower than the pressure in the gas turbine cylinder.
Further, in order to attain said second object, the present invention provides a steam cooled system in a combined cycle power plant constructed such that there is provided a control device for controlling a flow rate of cooling steam supplied into said steam cooled system, based on an outlet steam temperature of said steam cooled system and a fuel supply rate to said gas turbine.
That is, in view of the fact that the thermal load of the gas turbine high temperature portion to be cooled changes corresponding to the fuel supply rate to the gas turbine and yet the speed of such change is quick with a sensitive response, the fuel supply rate of the fuel supplied into the gas turbine _ g _ is made one control factor and in addition thereto, the outlet steam temperature of the steam cooled system is made another control factor, thus the steam flow rate of the cooling steam supplied into the steam cooled system is controlled appropriately.
In the combined cycle power plant employing the steam cooled system, it is preferable that occurrence of disorder, such as occurrence of cracks, clogging of steam system or the like, in the gas turbine high temperature portion is detected earlier by use of a temperature detecting signal of a high temperature portion outlet steam temperature detector so that a safe operation of the gas turbine may be effected.
Thus, the present invention provides an outlet steam monitoring system in a steam cooled type gas turbine, said steam cooled type gas turbine being constructed such that a cooling steam is supplied into a high temperature portion of combustor, blade or the like and the cooling steam after being used for cooling is recovered, characterized ir. 'hat there are provided a temperature detector for detecting an outlet temperature of 2~ said steam after being used for cooling and a control device which, being inputted a detected signal of said temperature detector for comparison with a predetermined temperature value, puts out a warning signal as well as a signal for throttling opening of a fuel flow control valve to a predetermined opening or a signal for closing a shut-off valve, if a detected temperature of said temperature detector exceeds said predetermined temperature value.
In the outlet steam monitoring system of the present invention, the outlet steam temperature of the steam which has cooled the high temperature portion is detected by the temperature detector and this detected signal is inputted into the control device. In the control device, the outlet steam temperature at the normal state, the temperature at the dangerous state, the upper limit temperature to shut off the fuel, etc. are set in advance and the detected temperature is compared therewith. If the detected temperature exceeds the set temperature, the warning signal, the signal for throttling the opening of the flow control valve and the signal for closing the shut-off valve are put out corresponding to the respective level of the temperature rise. Thereby, disorder in the high temperature portion is detected earlier and a dangerous state can be avoided by said signals of the control device.
BRIEF DESCRIPTION OF THE DRAWINGS:
Fig. 1 is a diagrammatic view showing construction of a steam cooled system in a combined cycle power plant of embodiment 1 according to the present invention.
Fig. 2 is a view of a cooling steam supply system and control system of gas turbine high temperature portion in a steam cooled system of embodiment 2 according to the present invention, wherein Fig. 2 ( a ) is a schematic view of arrangement of main components of the cooling steam supply system and Fig.
2(b) is a schematic view of a control circuit.
Fig. 3 is a diagrammatic view showing construction of a prior art steam cooled system in a combined cycle power plant.
Fig. 4 is a constructional view of an outlet steam monitoring system in a steam cooled type gas turbine of embodiment 3 according to the present invention.
Fig. 5 is a graph showing relationship between temperature states and control signals in the outlet steam monitoring system of the embodiment 3, wherein Fig. 5(a) shows the temperature states and Fig. 5(b) shows the control signals.
DESCRIPTION OF THE PREFERRED EMBODIMENTS:
Herebelow, a steam cooled system of the combined cycle power plant according to the present invention will be described concretely based on embodiments 1 and 2 shown in Figs .
1 and 2. It is to be noted that, in the embodiments below, same parts or components as those in the prior art shown in Fig. 3 are given same reference numerals for ease of description.
(Embodiment 1) Firstly, embodiment 1 shown in Fig. 1 will be described. In Fig. 1, a temperature control valve 12 is provided on an outlet side of cooling steam of a high temperature portion 8, such as combustor etc. Numeral 16 designates a high temperature portion outlet steam pressure detector and numeral 17 designates a gas turbine cylinder pressure detector. Construction thereof is made such that signals from these pressure detectors 16, 17 are given to a subtractor 20.
Numeral 18 designates a pressure controller, which receives output signal from the subtractor 20. Numeral 19 designates a lower value selector, which receives signals from a temperature controller 11 and the pressure controller 18 to select a lower value thereof. Other portions of the construction thereof are substantially same as those of the gas turbine steam cooled system shown in Fig. 3 and description thereon will be omitted.
In the gas turbine steam cooled system of Fig. 1 constructed as mentioned above, a signal showing a cooling steam temperature detected at a high temperature portion outlet steam temperature detector 15 is sent to the temperature controller 11 and the temperature control valve 12 is adjusted so as to set a high temperature portion outlet steam temperature to a predetermined set value.
That is, the temperature controller 11 generates a signal such that, if the cooling steam temperature at an outlet of the high temperature portion 8 is higher than the set value, the temperature control valve 12 is operated in the direction to open to increase flow rate of the cooling steam or reversely if the cooling steam temperature at the outlet of the high temperature portion 8 is lower than the set value, the temperature control valve 12 is operated in the direction to close to decrease the flow rate of the cooling steam.
On the other hand, a cooling steam pressure at the outlet of the high temperature portion 8 is detected by the pressure detector 16 and pressure in a gas turbine cylinder (discharge pressure of gas turbine air compressor) is detected by the pressure detector 17, respectively, and respective signals showing such measured pressures are inputted into the subtractor 20 to be subtracted therein. If there is recognized a tendency that the cooling steam pressure becomes lower than the pressure in the turbine cylinder, the pressure controller 18 generates a signal such that the temperature control valve 12 is operated in the direction to close.
The respective signals sent from the temperature controller 11 and the pressure controller 18 are inputted into the lower value selector 19 to be compared of their sizes and the lower value is selected to be put out as a signal to operate the temperature control valve 12. By use of the lower value selector 19 selecting the signals of the temperature controller 11 and the pressure controller 18, the temperature controller 11 can do control such that a rise of the cooling steam temperature at the outlet of the high temperature portion 8 is suppressed as much as possible within the range of the outlet steam pressure of the high temperature portion 8 not becoming lower than the pressure in the gas turbine cylinder.
(Embodiment 2) Next, embodiment 2 shown in Fig. 2 will be described.
In Fig. 2, only a construction around the gas turbine high temperature portion to be cooled by steam is shown and other - portions of the construction of the combined cycle power plant being substantially same as those shown in Fig. 1, description thereon will be omitted.
Fig. 2 ( a ) shows a portional equipment arrangement in a main part of a cooling steam flow. Numeral 21 designates a cooling steam supply passage, which supplies therethrough a high pressure turbine exhaust steam or a generated steam of a waste heat recovery boiler etc. (not shown) as a cooling steam.
Numeral 22 designates a temperature control valve provided in the cooling steam supply passage 21, which is controlled to be opened and closed by an opening and closing command E obtained in a control circuit as described later.
Numeral 23 designates a combustor disposed subsequently to the temperature control valve 22, numeral 24 designates a pressure control valve provided in a cooling steam recovery passage 27 and numeral 25 designates a pressure control valve provided in a condenser connection passage 26 which connects to a condenser (not shown).
Fig. 2 ( b ) shows a control circuit for generating said opening and closing command E, wherein an input command on one hand is a fuel control signal CSO (Control signal output) for controlling flow rate of fuel supplied into the combustor 23 and this fuel control signal CSO is first computed by function units 30, 31, 32 and 33, respectively.
Also, an input command on the other hand is an outlet steam temperature (actual temperature) of the combustor 23 and computation is done at a computing unit 34 which performs a proportional integration together with signals based on outputs of the function units 32, 33 and result thereof is added at an adder 35 to signals based on outputs of the function units 30, 31 so that said opening and closing command E is generated.
It is to be noted that the fuel control signal CSO
is corrected corresponding to a temperature of air charged for combustion etc . and an opening command value and a temperature set value of the temperature control valve 22 are decided based thereon so that a sudden change in the fuel control signal CSO
may be followed up well.
Also, the opening command value and the temperature set value, respectively, may be changed instantly by a fuel change-over command so that a change of the fuel may be followed up quickly.
Also, the temperature set value is computed in comparison with the actual temperature by a proportional integration computation (PI control) or by a proportional computation (P control) and result thereof is added to the opening command value, wherein there is set an upper limit in a direction of throttling and if the opening command is in saturation (100 or more), output of the proportional integration computation (PI) or the like is fixed to that value.
According to the present embodiment mentioned above, the cooling steam flow rate is controlled advance-wise based on a certain function setting corresponding to the fuel supply rate into the gas turbine. Thus, while in the method, for example, where the cooling steam flow rate is controlled relying only on the temperature of the cooling steam which has been used for cooling of the high temperature portion, there is a fear of delay due to thermal capacity of pipings etc.
downstream of the high temperature portion, there is no such a fear in the present embodiment and unusual excess cooling or heating can be prevented and a favorable cooling by steam, which suppresses occurrence of thermal stresses at the high temperature portion to be cooled, can be realized.
(Embodiment 3) An example as embodiment 3 where a monitoring system is constructed for monitoring an outlet steam temperature of a steam cooled type gas turbine using a temperature detecting signal of a combustor etc. high temperature portion outlet steam temperature detector will be described with reference to Figs. 4 and 5.
In Fig. 4, numeral 41 designates a steam supply manifold and numeral 42 designates a flow control valve, which controls flow rate of steam to be supplied. Numeral 43 designates a supply line, which supplies therethrough a cooling steam into a cooling steam supply pipe 65 of each of a plurality of combustor main bodies 60 from the steam supply manifold 41.
Numeral 44 designates a recovery line, numeral 45 designates a steam recovery manifold and steam recovered through the recovery line 44 from cooling steam recovery pipes 66, 67 of each of the plurality of combustor main bodies 60 is recovered into the steam recovery manifold 45.
Numeral 46 designates a temperature detector, which detects temperature of inlet steam flowing through the supply line 43 connecting to each of the plurality of combustor main bodies 60 to send a signal thereof to a control device 50 via an inlet steam temperature detecting line 47. Numeral 48 also designates a temperature detector, which detects temperature of the steam recovered flowing through the recovery line 44 from the cooling steam recovery pipes 66, 67 to send a signal thereof to the control device 50 via an outlet steam temperature detecting line 49.
Numeral 50 designates the control device mentioned above, numeral 51 designates a display for displaying result of computation at the control device 50 and numeral 52 designates a warning device for giving a warning by an alarm etc. when something wrong is found as the result of computation at the control device 50. Numeral 53 designates a control signal line, wherein a line 53a thereof transmits therethrough a signal to control opening of a flow control valve 55 of a fuel system 54 and a line 53b thereof transmits therethrough a signal to control opening and closing of a shut-off valve 56.
In the construction mentioned above, an inlet steam temperature detected by the temperature detector 46 of each of the combustors as the high temperature portions and an outlet steam temperature detected by the temperature detector 48 of the steam recovered from the cooling steam recovery pipes 66, 67 of each of the combustors are inputted into the control device 50.
Temperature of the steam supplied is approximately a planned supply steam temperature and temperature of the steam recovered is approximately a planned outlet steam temperature at a normal operation time. The control device 50 confirms whether the inlet steam temperature is normal as being approximately the planned supply steam temperature or not and then monitors the outlet steam temperature. While the outlet steam temperature is approximately the planned outlet steam temperature at the normal operation time, if there occurs an unusual case, such as clogging of steam passage, occurrence of cracks or the like, in the combustor main body, the temperature rises to a dangerous level or more to cause a dangerous situation, hence the control is done such that the situation of temperature is displayed on the display 51 as well as the signal thereof is sent to the warning device 52 so as to generate a warning.
If the situation of rising of the temperature continues, the control device 50 sends a control signal through the control signal line 53b to throttle opening of the flow control valve 55 so that the fuel in the fuel system is decreased to control the load, and if the temperature rises further to become higher than an upper limit temperature, for example a shut-off temperature, a control signal is put out through the control signal line 53a to control the shut-off valve 56 to be closed and the gas turbine is tripped.
Fig. 5 is an explanatory view of the situation mentioned above, wherein Fig. 5 ( a ) shows changes in the outlet steam temperature and Fig. 5(b) shows control signals corresponding to the temperature. In Fig. 5(a), the outlet steam temperature is in the state of approximately the planned outlet steam temperature at the normal operation time as shown by (X), and if the temperature rises beyond the dangerous temperature at time t1 as shown by ( Y1 ) , the control device 50 recognizes a dangerous situation of the combustor main body 60 to put out a warning signal (S1) as shown in Fig. 5(b) continuously during the time t1 to t2 exceeding the dangerous temperature and the warning device 51 is operated.
If the temperature continues to rise for a certain time until time t1' between the time t, to t2, the control device puts out a load decreasing signal (S,) as shown in Fig. 5(b) to control opening of the flow control valve 55 of the fuel system 54 to be throttled. If the temperature rises further to exceed the shut-off temperature at time t3 as shown by (YZ), a shut-off signal (S2) as shown in Fig. 5(b) is put out to close the shut-off valve 56 of the fuel system 54 so that fuel supply to a main fuel supply pipe 63 is stopped and the gas turbine is tripped.
It is to be noted that although the illustration of Fig. 4 is made in a form of omission on the example where the plurality of the combustor main bodies 60 are arranged in the common fuel system 54 to control the flow control valve 55 and the shut-off valve 56 commonly, needless to mention, it is necessary to control the flow control valve and the shut-off valve of the respective fuel system independently with respect to each of the combustor main bodies 60, wherein accident or disorder of each of the combustors is detected, flow rate of only the combustor on which disorder has been detected is controlled and the shut-off valve thereof is closed.
Also, in the present embodiment, although the example of the steam cooled combustor has been described, the invention is not limited thereto but may be applied to a temperature monitoring of an object to be cooled not only of the combustor but also of a stationary blade and a moving blade with same function and effect.
According to the present embodiment, temperature of the outlet steam recovered through the recovery line 44 from the cooling steam recovery pipes 66, 67 of the combustor main body 60 is detected by the temperature detector 48 to be inputted into the control device 50 so that the temperature rise is monitored by the control device 50 and if the outlet steam temperature exceeds the predetermined temperature, the warning device 52 is operated to generate a warning as well as the flow control valve 55 is controlled to control the fuel flow rate or to close the shut-off valve 56 to stop the fuel supply, thereby disorder of the combustor can be detected earlier by the change in the outlet steam temperature and a safe operation of the gas turbine can be ensured.
As described above with respect to the embodiments 1 and 2, in the steam cooled system of the combined cycle power plant according to the present invention, the construction is made such that there is provided the temperature control valve - at the cooling steam outlet of the high temperature portion of the gas turbine and this temperature control valve performs a cooling steam temperature control so that the temperature of the cooling steam coming out of the high temperature portion is set to the predetermined value as well as performs a cooling steam pressure control, which is preferential to said cooling steam temperature control, so that the pressure of the cooling steam coming out of the high pressure portion may not become lower than the pressure in the gas turbine cylinder.
According to this gas turbine steam cooled system, it is possible to effect a cooling by steam so that the temperature of the cooling steam coming out of the gas turbine high temperature portion may not become higher than the predetermined temperature within the range of the cooling steam pressure not becoming lower than the pressure in the gas turbine cylinder.
Also, according to the present invention constructed such that there are provided the cooling steam temperature control system for controlling the temperature control valve so that the cooling steam temperature at the cooling steam outlet of the gas turbine high temperature portion is set to the predetermined set value and the cooling steam pressure control system for controlling the temperature control valve so that the cooling steam pressure at the cooling steam outlet may not become lower than the pressure in the gas turbine cylinder and the temperature control valve is operated by the lower value out of the signals of these two control systems, a device in which the cooling steam pressure is securely maintained higher than the pressure in the gas turbine cylinder in preference to the control of the cooling steam temperature at the outlet of the gas turbine high temperature portion by a simple construction can be realized.
Also, according to the present invention constructed otherwise, based on the experience and knowledge of the inventors here that the thermal load of the gas turbine high temperature portion to be cooled changes corresponding to the fuel supply rate and the speed of such change is comparatively quick, the construction is made such that the cooling steam side is also controlled with a good response corresponding to the fuel supply rate. That is, according to this invention, the fuel supply rate to the gas turbine and the outlet steam temperature of the steam cooled system are employed as the control factors and the flow rate of the steam supplied into the steam cooled system is controlled appropriately so that the gas turbine high temperature portion may not be cooled or heated excessively and occurrence of the thermal stresses at said high temperature portion may be suppressed. Hence, a device which can be operated safely and stably for a long time is realized and a reliability of the plant can be enhanced remarkably.
Further, as described concretely based on the embodiment 3 , the outlet steam monitoring system according to the present invention is used in the steam cooled type gas turbine which is constructed such that the cooling steam is supplied into the high temperature portion of combustor, blade or the like and the cooling steam after used for cooling is recovered, and is characterized in that there are provided the temperature detector for detecting the outlet temperature of the steam after used for cooling and the control device which, being inputted a detected signal of the temperature detector for comparison with the predetermined temperature value, puts out a warning signal as well as a signal for throttling opening of the fuel flow control valve to the predetermined opening or a signal for closing the shut-off valve, if a detected temperature of the temperature detector exceeds the predetermined temperature value. By employing such construction, upon the change in the outlet temperature of the steam after used for the cooling, disorder of the high temperature portion can be detected earlier as well as the control signal can be put out from the control device so that danger may be avoided.
Claims (4)
1. A steam cooled system in a combined cycle power plant, said combined cycle power plant comprising a combination of a gas turbine plant and a steam turbine plant, a waste heat recovery boiler (2) for generating a steam turbine driving steam using waste heat of a gas turbine (1), a steam cooled system using steam for cooling a high temperature portion (8) of said gas turbine (1) and a steam recovery system for recovering superheated steam coming from said steam cooled system into a steam turbine, characterized in that there is provided a temperature control valve (12) at a cooling steam outlet of said high temperature portion (8) and said temperature control valve (12) performs a cooling steam temperature control so that temperature of cooling steam coming out of said high temperature portion (8) is set to a predetermined value as well as performs a cooling steam pressure control, which is preferential to said cooling steam temperature control, so that pressure of the cooling steam coming out of said high temperature portion (8) may not become lower than pressure in a turbine cylinder of said gas turbine (1).
2. A steam cooled system in a combined cycle power plant, said combined cycle power plant comprising a combination of a gas turbine plant and a steam turbine plant, a waste heat recovery boiler (2) for generating a steam turbine driving steam using waste heat of a gas turbine (1), a steam cooled system using steam for cooling a high temperature portion (8) of said gas turbine (1) and a steam recovery system for recovering superheated steam coming from said steam cooled system into a steam turbine, characterized in that there are provided a temperature control valve (12) at a cooling steam outlet of said high temperature portion (8), a cooling steam temperature control system (11, 15) for controlling said temperature control valve (12) so that a cooling steam temperature at said cooling steam outlet is set to a predetermined value and a cooling steam pressure control system (16, 17, 18, 20) for controlling said temperature control valve (12) so that a cooling steam pressure at said cooling steam outlet may not became lower than pressure in a turbine cylinder of said gas turbine (1) and said temperature control valve (12) is operated by a lower value out of control signals of said temperature control system (11, 15) and said pressure control system (16, 17, 18, 20).
3. A steam cooled system in a combined cycle power plant, said combined cycle power plant comprising a combination of a gas turbine plant and a steam turbine plant, a waste heat recovery boiler (2) for generating a steam turbine driving steam using waste heat of a gas turbine (1), a steam cooled system using steam for cooling a high temperature portion of said gas turbine (1) and a steam recovery system for recovering superheated steam coming from said steam cooled system into a steam turbine, characterized in that there is provided a control device for controlling a flow rate of cooling steam supplied into said steam cooled system, said control device being a control circuit for the generation of an output command (E) from two input commands, namely a fuel control signal (CSO) for controlling a low rate of fuel supplied into said gas turbine (1) and an outlet steam temperature of said steam cooled system, wherein said fuel control signal (CSO) is fed into a function unit (30 to 33) to generate output signals which are then fed into a computing unit (34, 35) together with said outlet steam temperature to generate said output command (E).
4. An outlet steam monitoring system in a steam cooled type gas turbine, said steam cooled type gas turbine being constructed such that a cooling steam is supplied into a high temperature portion of combustor, blade or the like and the cooling steam after being used for cooling is recovered, characterized in that there are provided a temperature detector (48) for detecting an outlet temperature of said steam after being used for cooling and a control device (50) which, being inputted a detected signal of said temperature detector (48) for comparison with a predetermined temperature value, puts out a warning signal as well as a signal for throttling opening of a fuel flow control valve (55) to a predetermined opening or a signal for closing a shut-off valve (56), if a detected temperature of said temperature detector exceeds said predetermined temperature value.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP01681198A JP3881762B2 (en) | 1998-01-29 | 1998-01-29 | Gas turbine steam cooling system |
| JP10-016811 | 1998-01-29 | ||
| JP2814998A JPH11229896A (en) | 1998-02-10 | 1998-02-10 | Combined cycle electric power plant |
| JP10-028149 | 1998-02-10 | ||
| JP19032798A JP3735203B2 (en) | 1998-07-06 | 1998-07-06 | Steam monitoring system for steam cooled gas turbine |
| JP10-190327 | 1998-07-06 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2260415A1 CA2260415A1 (en) | 1999-07-29 |
| CA2260415C true CA2260415C (en) | 2002-07-23 |
Family
ID=27281574
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002260415A Expired - Fee Related CA2260415C (en) | 1998-01-29 | 1999-01-27 | Steam cooled system in combined cycle power plant |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US6324829B1 (en) |
| EP (3) | EP1182330B1 (en) |
| CA (1) | CA2260415C (en) |
| DE (2) | DE69930557T2 (en) |
Families Citing this family (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4698860B2 (en) * | 2000-04-18 | 2011-06-08 | 三菱重工業株式会社 | Turbine steam control device |
| CA2364125C (en) * | 2000-11-28 | 2005-05-24 | Mitsubishi Heavy Industries, Ltd. | Steam cooling apparatus for gas turbine |
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-
1999
- 1999-01-22 EP EP01126611A patent/EP1182330B1/en not_active Expired - Lifetime
- 1999-01-22 DE DE69930557T patent/DE69930557T2/en not_active Expired - Lifetime
- 1999-01-22 DE DE69931413T patent/DE69931413T2/en not_active Expired - Lifetime
- 1999-01-22 EP EP99101211A patent/EP0933505B1/en not_active Expired - Lifetime
- 1999-01-22 EP EP06100284A patent/EP1752618A3/en not_active Withdrawn
- 1999-01-27 CA CA002260415A patent/CA2260415C/en not_active Expired - Fee Related
- 1999-01-27 US US09/237,845 patent/US6324829B1/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| EP1752618A3 (en) | 2012-06-27 |
| DE69931413T2 (en) | 2007-05-03 |
| EP0933505A2 (en) | 1999-08-04 |
| EP0933505B1 (en) | 2006-05-24 |
| US6324829B1 (en) | 2001-12-04 |
| EP1182330A1 (en) | 2002-02-27 |
| CA2260415A1 (en) | 1999-07-29 |
| DE69930557D1 (en) | 2006-05-18 |
| EP1182330B1 (en) | 2006-03-29 |
| EP1752618A2 (en) | 2007-02-14 |
| DE69931413D1 (en) | 2006-06-29 |
| EP0933505A3 (en) | 2002-03-20 |
| DE69930557T2 (en) | 2006-12-28 |
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